Fluid engine compensator device



Nov. 9, 1965 c, BAKER 3,216,190

FLUID ENGINE GOMPENSATOR DEVICE Filed June 13, 1962 2 Sheets-Sheet lINVENTOR CHARLES H. BAKER wmw A TTORNE Y Nov. 9, 1965 c. H. BAKER3,216,190

FLUID ENGINE COMPENSATOR DEVICE Filed June 15, 1962 2 Sheets-Sheet 2 XI32 F I28 I24 FIG. 3 30 I06 I ,5

36 I 34 68 INVENTOR.

28 CHARLES H. BAKER BY X ATTORNEY United States Patent Ofifice 3,216,190Patented Nov. 9, 1965 3,216,190 FLUKE) ENGINE COMPENSATOR DEVICE CharlesH. Baker, Cleveland, Ohio, assignor to Cleveland Pneumatic industries,Inc, Cleveland, Ohio, 21 corporation of Ohio Filed June 13, 1962, Ser.No. 202,285 29 Claims. (Cl. 6024) This invention relates tothermodynamic engines in which working fluids traverse a thermodynamiccycle to produce power and more particularly, pertains to novel orimproved apparatus for maintaining the horsepower output of such enginesconstant by compensating for variations in the temperature of heatingand cooling sources associated therewith and for substitution in thetype of working fluid utilized in the operating cycle thereof.

In a fluid-type engine of the type disclosed herein, a working fluid,compressed and heated, is expanded against a working surface within anexpansion chamber of a piston-cylinder arrangement to produce mechanicalpower. The working fluid, in an initial condition, is compressed thenheated and subsequently directed to the expansion chamber whereat theworking fluid expands against the working surface of the piston-cylinderarrangement surface. After expansion, and at a reduced temperature andpressure, the working fluid is directed to a unit whereat the workingfluid is cooled to the initial (before compression) condition. In afluid engine of this type, the above set forth thermodynamic cycle istraversed by a suitable working fluid having desirable volumetricexpansion characteristics and advantageous thermal properties. In thepast, fluid-type engines were specifically designed for a particulartype of working fluid and wherein the temperatures of the heating andcooling sources remained constant. However, in the event a differentworking fluid was contemplated, the specific heating source as well asthe cooling source would be inadequate to obtain the desired output fromthe fluid-type engine depending upon the properties of the workingfluid. Further, where a particular working fluid is employed and thecorresponding required heating and cooling sources are not available, anentirely new fluid-type engine redesigned for the available powersources would be necessary to compensate for any variation in operatingtemperatures at each site of application of the fluid-type engine.

By providing apparatus in the form of a compensator device to readilycompensate for any substitution of working fluid as well as thetemperature variations in the available heating and cooling sources, asingle fluid-type engine design may be utilized for a multiplicity ofapplications in which these variables are prevalent. For example, ininstances where a fluid-type engine has been designed for a particularworking fluid such as carbon dioxide, requiring specific heat source andcooling source capabilities applicable to CO any change in the workingfluid or temperatures of the power sources would require a correspondingchange in the fluid-type engine design. However, by utilizing theinventive compensator device described, disclosed, shown and illustratedherein such compensations without complete redesign of the fluid-typeengine can be readily made. Where the operating temperatures ofavailable heat sources are below a required amount, for effectiveoperation of the working fluid, the compensator device of the apparatusmay be readily adjusted to increase the pressure of the working fluid inthe compression chamber. Thus the working fluid can be transmitted tothe lower temperature heat source and receive an amount of heatproportional to the increased pressure thereof resulting in the requiredvolumetric expansion in the working fluid and accordingly maintainconstant horsepower output of the fluid-type engine as though thetemperature of the heat source originally specified were available. Inlike manner, in a substitution of working fluid having differenttemperature and pressure requirements for optimum volumetric expansion,a change in the thermodynamic cycle to compensate for same is readilyobtained by controlled operation of the compensator device of theapparatus. The compensator device permits the fluid-type engine tofunction properly with a constant desired horsepower output irrespectiveof the working fluid utilized or the variation in the operatingtemperatures of the heating and cooling sources available at suchlocations where the fluid-type engine is being utilized.

Therefore, it is the principal object of this invention to provideapparatus in the form of a device cooperable with a fluid-type engine inwhich a working fluid traverses a thermodynamic cycle with such devicebeing operable to compensate for the use of more than one type ofworking fluid having different temperature characteristics for which thefluid-type engine was designed.

It is another object of this invention to provide apparatus in the formof a device cooperable with a fluid-type engine in which a working fluidtraverses a thermodynamic cycle with such device being operable tocompensate for temperature variations of available heating and coolingpower sources at the respective installation site of the fluid-typeengine.

A further object of this invention is to provide a compensating devicecooperable with a fluid-type engine in which a working fluid traverses athermodynamic cycle wherein the device permits the utilization of aspecific working fluid in a variety of thermodynamic cycles ofoperation.

These and other objects and important features of the invention will beapparent from a study of the specification following taken with thedrawing, which together show, illustrate, describe and disclose certainpreferred embodiments and modifications of the invention and what is nowconsidered to be the best mode of practicing the principles thereof.Other embodiments or modifications may be suggested to those having thebenefit of the teaching herein, and all such embodiments ormodifications are intended to be reserved as they fall within the spiritand scope of the subjoined claims.

In the drawing:

FIGURE 1 is a schematic illustration, partially in crossection, of asystem having a fluid-type engine employing a thermodynamic cycleshowing apparatus incorporated therewith for compensating for certainconditions and factors which may exist in a working fluid of the system.

FIGURE 2 is an enlarged, longitudinal sectional view of the apparatusassociated with the fluid-type engine as illustrated in FIGURE 1 of thedrawing and showing in more detail a compensator device of theapparatus, and

FIGURE 3 is an enlarged, longitudinal sectional view similar to FIGURE 2of the drawing showing a modification or additional embodiment of thecompensator device of the apparatus.

Attention is now directed to FIGURE 1 of the drawing, wherein a systemltl is illustrated in partial schematic form wherein the system 10, isin effect, closed and comprises, as a part thereof, a fluid-type engine12 having a block 14 in which a cylinder 16 is bored and a piston 18 isreciprocably mounted. The piston 18 is secured to a connecting rod 20and a crankshaft 22 arrangement disposed in a crankcase chamber 25formed by a housing 26. The piston 18 comprises an enlarged base portion28 and an extended reduced portion 30 forming a shoulder 32therebetween. The shoulder 32 has a Working surface 34, (note FIGURES 2and 3 of the drawing), thereon forming one wall of a compression chamber36 and the extended reduced portion has a working surface 38 thereonforming one wall of an expansion chamber 40. The structural details ofthe piston 18 and the arrangement thereof with the engine block 14 aremore specifically described, disclosed, shown, illustrated and claimedin the US. application Serial Number 213,401, filed July 30,1962, nowPatent No. 3,174,276, filed in the name of the instant inventor andassigned to the assignee of the present invention.

The compression chamber 36 has an inlet port 42 and an outlet port 44circumferentially spaced and suitably arranged about the engine block 14with the ports 42 and 44 each being communicable with the compressionchamber 36. The outlet port 44 has a check valve 46 communicabletherewith wherein working fluid F from the compression chamber isdirected through the outlet port 44 and the check valve 46 into aconduit 48 and thence into the power heat exchanger 50. Disposedintermediate the outlet valve 46 and the power heat exchanger 50 is avalve 52 and an accumulator 54 arrangement, which functions to providerapid starting of the fluid-type engine 12 after shutdown. A conduit 56connects the power heat exchanger 50 to an inlet valve 58 disposedadjacent one end portion of the engine block 14 in communication withthe expansion chamber 40. An outlet valve 60 is also disposed at the oneend portion of the engine block adjacent the inlet valve 58 to providecommunication of the working fluid F in the expansion chamber 40 with aconduit 62. The conduit 62 directs the working fluid F from theexpansion chamber 40 into a cooling heat exchanger 64 and therefromthrough a conduit 66 into an inlet valve 68 connected to the inlet port42 communicable with the compression chamber 36.

A bypass valve 70 is disposed in the conduit 62 intermediate the outletvalve 60 and the cooling heat exchanger 64 and communicates through asuitable conduit 72 with the conduit 66 and the inlet valve 68. An oilseparator 73 is connected to the conduit 62 intermediate the bypassvalve 70 and the cooling heat exchanger 64. The oil separator '73functions to separate the lubricating oil from the working fluid withwhich it passes through the system 10 during the operating cyclethereof. The oil separator 73 is connected to a filter 74 which isconnected to the engine crankcase housing 26 by suitable conduits. Thelubricating oil enters into the system by conventional pumping meanswhich directs the oil from the crankcase into the piston and throughsuitable passageways (not shown). Lubricating oil as directed, isthereby disposed onto the cylinder walls and into the compressionchamber becoming commingled with the working fluid. The specific detailsof the oil separator 73 and the filter 74 in combination with the system10 is more fully described, disclosed, shown, illustrated and claimed inthe US. application Serial Number 191,075 filed April 30, 1962., nowPatent No. 3,138,918, in the name of the instant inventor and assignedto the assignee of the present invention.

In order to compensate for certain conditions or factors, such asvariations in the temperature of the working fluid F resulting from theeffect created thereon by the power heat exchanger 50 and the effectivecooling of the working fluid F resulting from the heat exchanger 64, aswell as providing for the substitution of different types of workingfluid which may be employed in the system 10 to operate the fluid-typeengine 12, there is provided apparatus which may take the form of acompensator or engine multiplier device 75 (FIG. 2) which comprises ahousing 76 having an externally threaded portion 78 thereon cooperablewith a correspondingly internally threaded portion 80 of a recess 81formed in the engine block 14. A chamber 82 is defined by the recess 81and the multiplier housing 76 with the multiplier device 75 beingconnected to the block 14 through the threaded engagement of theportions 78, 80. A freely movable piston member 84, responsive topressures of the compression chamber 36, is reciprocably mounted in abore 86 formed in the housing 76 and comprises a pair of cylindricalportions 88 and 90 separated by a necked down portion 91 disposedtherebetween. An annular shoulder 92 is formed by the housing 76 and isengageable with cylindrical portion 88 of the piston member 84 torestrict axial movement thereof in an inwardly direction. Thecylindrical portion 88 of the piston member 84 has an integrally formedextended portion 94 projecting therefrom for engagement with a surface96 formed'on a cam member 98 disposed in a cavity 99 formed by thehousing 76. The cam member 98 is suitably secured to a camshaft 100wherein the camshaft 166) is operably connected to means (not shown) forproviding the desired rotative movement in the camshaft 160 which willbe effective to reciprocate the piston member 84 through the engagementof the cam member 98 therewith in the housing 76 of the multiplierdevice 75. 0 rings 101 and 102 are disposed on the cylindrical portions88 and 90 respectively, and provide a fluid seal restricting the passageof the working fluid F past the piston member 84 and into the cavity 99.A projection 103 is formed on the other end of the piston member 84integral with the cylindrical portion 90 and reciprocates therewithwithin a passage defining a chamber 194 formed in the correspondinglythreaded portion 78 of the housing 76, responsive to the actuation ofthe cam member 98. A passage 106 is formed in the engine block 14 withone end 108 thereof communicable with the inlet port 42 of thecompression chamber 36 and the other end 110 thereof communicable withthe recess chamber 82 and the chamber 104 formed in the threaded portion70 of the multiplier housing 76. Thus the compression chamberarrangement comprises the chamber 36 as well as the passage 106, recesschamber 82 and the chamber 104 formed in the multiplier device 75.

The fluid-type engine 12 as shown, discloses a single piston 18 andcylinder 16 arrangement, however, it is within the scope of theinvention described herein to provide a multiplicity of such piston andcylinder arrangements within the engine block 14 and correspondinglyprovide a compensator or multiplier device 75 in communication with eachcompression chamber 36 of a multiple piston and cylinder embodiment.

The operational cycle of the fluid-type engine 12 will be described tobest illustrate the inventive concept disclosed, described, shown andillustrated herein and accordingly the cycle will be described only tothe extent necessary for a complete understanding of the presentinvention. Values for the temperatures and pressures experienced by theworking fluid F are merely exemplary and constitute representativeamounts for illustrative purposes only. In operation, a unit mass ofworking fluid P such as carbon dioxide at a temperature of approximately70 F., is compressed in the compression chamber 36 to a pressure ofapproximately 6,000 p.s.i. and a temperature of approximately 300 F. Atthis temperature and pressure the carbon dioxide is directed through theoutlet port 44, the outlet valve 46 and into the conduit 48. The valve46 is actuated by suitable means (not shown) and synchronized inrelationship to the cooperating elements of the cycle during engineoperation. The compressed working fluid in the conduit 48 is directedthrough the valve 52 of the accumulator arrangement 54 and into thepower heat exchanger 50 in which heat from any suitable source isapplied to the working fluid F to substantially raise its temperature toapproximately 500 F. while the pressure remains substantially constant.At this temperature and pressure, the carbon dioxide enters the inletvalve 58, through conduit 56 and upon synchronized opening of the inletvalve 58 by suitable means (not shown) the working fluid F is directedto the expansion chamber 40. When the working fluid enters the expansionchamber 40, the increased volume thereof enables the carbon dioxide toexpand so that a given mass of working fluid F has a greater volume whenit enters the expansion chamber 40 than it has as it is pumped out ofthe compression chamber 36. This expansion reduces the presssure and inturn reduces the temperature adiabatically. The piston 18 at this stageof operation, is in the top dead-center position but upon expansion ofthe carbon dioxide, is moved downwardly against the connecting rod 20and the crankshaft 22 arrangement imparting rotative movement to thecrankshaft. Upon continued rotation of the crankshaft 22, through therotation of a flywheel (not shown) attached thereto, the piston 18 isdirected upwardly and the outlet valve 60 is opened allowing the escapeof the expanded carbon dioxide at a reduced temperature and pressure ofapproximately 200 F. and 800 p.s.i. respectively, from the expansionchamber into the conduit 62 through the bypass valve 70 arrangement andinto the Cooling heat exchanger 64. The bypass valve 70 comprises meansfor controlling the speed of the fluid-type engine 12 and the detailsthereof are more specifically described, disclosed, illustrated, shown.and claimed in the U. S. application Serial Number 212,831 filed July27, 1962, now Patent No. 3,180,081, in the name of the instant inventorand assigned to the assignee of the present invention. Upon leaving thecooling heat exchanger 64, the working fluid F is reduced to atemperature of approximately 70 F. and a pressure of 800 p.s.i. andenters the inlet valve 68 through the conduit 66. Simultaneously withthe expansion stroke, the inlet valve 68 is opened to permit the carbondioxide at the low temperature and pressure values to enter thecompression chamber 36 whereupon the cycle is then repeated.

The valve 52 and the accumulator 5'4 arrangement disposed in the conduit48 comprises means for starting the fluid-type engine 12 after it hasbeen shutdown. A detailed description of the valve 52 and theaccumulator arrangement 54 and the advantages thereof are morespecifically claimed in the U. S. application Serial Number 222,729filed Sept. 10, 1962, now Patent No. 3,200,- 581, in the name of StanleyA. Welland and assigned to the assignee of the present invention.

The object and advantages of the compensator or multiplier device 75 canbest be described with reference to the operating cycle hereinabove setforth. If the power heat exchanger 50, due to the limitations in theavailable heat source, is incapable of supplying the desired amount ofheat to raise the temperature of the compressed working fluid F andconstant horsepower output must be maintained for the specifiedfluid-type engine application, manipulation of the camshaft 100 willcause the multiplier piston 84 to be directed inwardly towards thecompression chamber 36 whereby the chamber 82 formed between the housing76, the recess 81 and the extending portion 102 of the piston 84 will besubstantially reduced in volume. The inwardly directed movement of thepiston 84 and the reduction in the volume of the chamber 82 reduces theoverall dimensions of the compression chamber 36 whereby the compressionstroke of the piston 18 with the volumetric displacement thereof beingconstant will accordingly compress a unit mass of fluid F, occupying asmaller volume and accordingly being more dense, to a higher unitpressure. Upon opening the outlet valve 46, the working fluid F at asubstantially higher pressure will enter the power heat exchanger andaccordingly the available heat, being less than the amount requiredunder higher pressure conditions, is applied to the carbon dioxide,resulting in the desired volumetric expansion in the expansion chamber40 to maintain constant horsepower output of the fluid-type engine 12.In like manner; when the temperatures of the available heat source forthe power heat exchanger 50 are high in comparison to the operatingtemperatures required for the optimum volumetric expansion of the carbondioxide,

6 actuation of the camshaft in the opposite direction will displace thesurface 96 of the cam 98 such as to allow the piston 84 to moveoutwardly responsive to pressures of the carbon dioxide in thecompression chamber 36. Movement of the multiplier piston 84 in thisdirection increases the overall volume of the compression chamber 36 andaccordingly the working fluid F within the compression chamber 36 for aunit mass of carbon dioxide will occupy a larger volume and accordinglybe less dense due to the increased volume of the compression chamber 36.Therefore, a lower unit pressure will be obtained upon compression. Uponopening of the outlet valve 46, the working fluid F directedtherethrough into the conduit 48 and into the power heat exchanger 50will require receiving a greater amount of heat to compensate for thereduced pressure in order to maintain the desired volumetric expansionduring the piston power stroke to maintain constant horsepower output.The capabilities of the power heat exchanger 50 being such in thisexample that the necessary heat is available and accordingly raise thetemperature of the working fluid F by a proportional amount to oflsetthe lower pressures.

It can be readily seen from the above set forth description of theoperation of the multiplier device 75, that a specific working fluid canbe made to traverse a variety of thermodynamic cycles by manipulation ofthe multiplier device 75 and further the substitution of a differentworking fluid having different characteristics and properties can bereadily compensated for by the use of the multiplier device 75.

The fluid-type engine 12 having the apparatus comprising the multiplieror compensating device 75, may be actuated either by mechanical means ora manual type control mechanism such as disclosed in a modification orother embodiment thereof which is illustrated in FIGURE 3 of thedrawing. A manually adjustable multiplier device 112 comprising ahousing having a body member 114 provided with an externally threadedportion 116 thereon and a passage defining a chamber 118 formed thereinextending throughout the axial length of the body member 114. A shoulder120 is formed intermediate the engine block 14 and the externallythreaded portion 116 of the body member 114 and is adaptable to engagethe engine block. One end of the body member 114 has an externallythreaded portion 122 thereon cooperating with a corresponding internallythreaded portion 124 in the recess chamber 82 of the engine block 14.The housing of the multiplier device 112 also has a sleeve 126 providedwith an internally threaded portion 128 thereon for engagement with thethreaded portion 116 of the body member 114. A handle or wheel member130 is fixed to the sleeve 126 and upon rotation thereof, the sleeve 126will move axially inwardly or outwardly depending upon the direction ofrotation of the handle member 130. A freely movable piston member 132 isdisposed within the passage defining a chamber 118 of the body member114 and is reciprocable therein responsive to the pressure of the carbondioxide developed in the compression chamber 36. The handle member 130has a V shaped groove or recess 134 formed therein engagable with a stemportion 136 of the piston member 132 and acts as an abutting meansrestricting the axial movement of the piston member 132 within thechamber 118. An 0 ring 138 is disposed on one end 140 of the pistonmember 132 and prevents passage of fluid thereabout into a cavity 142formed between the sleeve 126 and the body member 114. The O ring 138 sodisposed, maintains the pressurized working fluid F within the recesschamber 82 formed by the engine block 14 and the multiplier body 114 andthe chamber 118 formed by the multiplier body 114, thereby controllingthe effective volume of the compression chamber 36 through thecommunication of passage 106 with the recess chamber 82 and chamber 118.It can be readily seen that in 7 situations Where manual control may bemaintained con stant through manipulation of the handle member 130 andaccordingly the sleeve 136 to enlarge or reduce the chamber 118.

While the invention has been described, disclosed, illustrated and shownin terms of certain embodiments or modifications, which it has assumedin practice, the scope of the invention should not be deemed to belimited by the precise certain embodiments and modifications hereindescribed, disclosed, illustrated and shown, since other embodiments andmodifications are intended to be reserved where they fall within thescope of the claims herein appended.

I claim as my invention:

1. Apparatus for controlling output of a fluid-type engine in which aworking fluid traverses a thermodynamic cycle of compression, heating,expansion and cooling stages, said apparatus comprising;

a housing defining a chamber, said chamber being disposed to receive aportion of said working fluid therein with said working fluid beingcommunicable with said chamber during the compression stage of saidcycle, and

means for effecting pressure variation in said working fluid within saidchamber.

2. Apparatus for controlling output of a fluid-type engine in which aworking fluid traverses a thermodynamic cycle according to claim 1wherein said means comprise a piston and cylinder arrangement operablydisposed within the housing.

3. Apparatus for controlling output of a fluid-type engine in which aworking fluid traverses a thermodynamic cycle according to claim 2wherein said piston is disposed in said cylinder and is operable toreciprocate therein.

4. Apparatus for controlling output of a fluid-type engine in which aworking fluid traverses a thermodynamic cycle according to claim 3wherein said piston is freely movable in said cylinder in one directionresponsive to pressure of such fluid in said cylinder and movable in anopposite direction responsive to means engageable with said piston.

5. Apparatus for controlling output of a fluid-type engine in which aworking fluid traverses a thermodynamic cycle according to claim 4wherein said means engageable with said piston comprises: a cam member,actuation means cooperable with said cam member eflfective uponactuation to move said piston in said cylinder in one direction and torestrict movement of said piston in said cylinder in an oppositedirection.

6. In combination with a fluid-type engine in which a Working fluidtraverses a thermodynamic cycle of compression, heating, expansion andcooling and having a piston and cylinder arrangement defining anexpansion and compression chamber, apparatus LfOI controlling the outputof said engine comprising:

a housing defining a recess chamber, said recess chamber being disposedin communication with said compression chamber of said engine andoperable to receive a portion of said working fluid therein; and

means cooperable with said recess chamber effective to vary the pressureof said working fluid in said compression chamber.

7. In combination with a fluid-type engine in which a fluid traverses athermodynamic cycle of compression, heating, expansion and coolinghaving a piston and cylinder arrangement defining an expansion andcompression chamber, apparatus for controlling said engine outputcomprising:

a housing defining a recess chamber, said recess chamber being disposedin communication with said compression chamber to receive a portion ofsaid working fluid therein from said compression chamber;

a piston member cooperable with said housing and re ciprocable withinsaid recess chamber,

cam means engageable with said piston member and operable upon actuationto impart movement to said piston member in one direction to reduce thevolume of said recess chamber and to increase the volume of said recesschamber in an opposite direction, said piston member being effectiveupon movement thereof to vary the pressure of said working fluid in saidcompression chamber.

8. In combination with a fluid-type engine in which a fluid transversesa thermodynamic cycle of compression, heating, expansion and cooling andhaving a piston and cylinder arrangement defining an expansion andcompres-. sion chamber, apparatus for controlling said engine outputaccording to claim 7, wherein said'cam means is automatically actuated.

9. In combination with a fluid-type engine in which a fluid traverses athermodynamic cycle of compression, heating, expansion and cooling, andhaving a piston and cylinder arrangement defining an expansion andcompression chamber therebetween, apparatus for controlling said engineoutput comprising;

a housing defining a recess chamber disposed in communication with saidcompression chamber to receive a portion of said Working fluid thereinfrom said compression chamber,

a piston member reciprocable in said housing; and

a manually controlled movable sleeve member engageable with said pistonmember and operable upo-n actuation to impart movement to said pistonmember in one direction and restrict movement thereof in an oppositedirection and effective to vary the pressure of said working fluid insaid compression chamber.

10. In combination with a fluid-type engine in which a fluid traverses athermodynamic cycle of compression, heating, expansion and cooling andhaving a piston and cylinder arrangement defining an expansion andcompression chamber therebetween, apparatus for controlling said engineoutput according to claim 9 wherein said housing comprises a bodymember, a chamber formed by said body member and a piston memberreciprocable in said body member and a movable sleeve member engageablewith said body member.

11. In combination with a fluid-type engine in which a fluid traverses athermodynamic cycle of compression, heating, expansion and cooling andhaving a piston and cylinder arrangement defining an expansion andcompression chamber therebetween, apparatus for controlling said engineoutput according to claim 10 wherein said movable sleeve member has athreaded portion thereon engageable with a correspondingly threadedportion on said body member.

12. In combination with a fluid-type engine in which a fluid traverses athermodynamic cycle of compression, heating, expansion and cooling andhaving a piston and cylinder arrangement defining an expansion andcompression chamber therebetween, apparatus for controlling said engineoutput according to claim 10, wherein said movable sleeve member ismounted for rotation on said body member and has a gripping portion toeffect axial movement in said sleeve with respect to said body member toincrease the volume of said recess chamber in one direction of rotationand to decrease the volume of said recess chamber in an oppositedirection of rotation thereof.

13. In combination with a fluid type engine in whlch a working fluidtraverses a thermodynamic cycle comprising the stages of compression,heating, expansion and cooling, and having:

engine block structure defining a bore therewithin;

piston structure disposed within said bore for longitudinal reciprocalmovements relative thereto between a plurality of positions therewithin;and

compression chamber structure disposed within said engine blockstructure, said chamber structure comprising:

a plurality of variable volume chambers;

one of said variable volume chambers being defined by and between saidengine block structure and said piston structure; compensator apparatusparticularly adapted to be structurally operatively associated with saidengine block structure, enabling the compensation for variations intemperatures and Working fluids utilized in said thermodynamic cycle,and further enabling said engine to maintain and present a substantiallyconstant output, said compensator comprising: a housing structurallyoperatively associated with said engine block structure; said housingand block structure defining another of said variable volume chambers;and pressure responsive structure disposed in said housing responsive tothe pressures within said compression chamber structure. 14. In thecombination as defined in claim 13, wheresaid pressure responsivestructure comprises: a plurality of portions; and a projection extendingfrom one of said portions in a direction generally towards the one ofsaid plurality of variable volume chambers; the diametral dimensionalextent of said projection being less than that of said portions,enabling the pressures within said one chamber to be directed againstthe one of said plurality of portions. 15. In the combination as definedin claim 14, wheresaid pressure responsive structure is reciprocalwithin said housing between a plurality of positions; said housing isprovided with a shoulder for defining one of said plurality ofpositions, and wherein there is provided: adjustable structure fordefining the other of said plurality of positions. 16. In thecombination as defined in claim 15, wheresaid adjustable structurecomprises: a rotatable cam disposed within said housing; and saidpressure responsive structure comprises further: an other projectionextending from the other of said plurality of portions generally in adirection towards said cam; said other projection being particularlyadapted to be mutually cooperatively engageable with a surface on saidcam. 17. In the combination as defined in claim 13, wheresaid pressureresponsive structure is reciprocal within said housing; and whereinthere is provided: adjustable structure for defining at least oneposition of the pressure responsive structure within said housing, andadjustable structure comprising:

a sleeve disposed in threaded mutual cooperative engagement with saidhousing; and

a handle structurally operatively associated with said sleeve;

said pressure responsive structure being mutually cooperativelyengageable with said handle.

18. Compensator apparatus particularly adapted to be structurallyoperatively associated with a fluid type engine in which a working fluidtraverses a thermodynamic cycle comprising the stages of compression,heating, expansion and cooling, and comprising:

a housing particularly adapted to be structurally operatively associatedwith the engine block structure of said engine;

pressure responsive structure disposed in said housing, said pressureresponsive structure being particularly adapted to be reponsive to thepressures within compression chamber structure in said engine, and beingreciprocally movable in said housing between a plurality of positionstherewithin and with respect thereto; and

adjustable structure for defining one of said plurality of positions.

19. The compensator apparatus as defined in claim 18,

wherein:

said pressure responsive structure comprises:

a plurality of portions; and

a projection extending from one of said portions;

the diametral dimensional extent of said projection being less than thatof said portions, enabling the pressures within said compression chamberstructure to be directed against the one of said plurality of portions.

20. The compensator apparatus as defined in claim 19,

wherein:

said adjustable structure comprises:

a rotatable cam disposed within said housing; and

said pressure responsive structure comprises further:

an other projection extending from the other of said plurality ofportions generally in a direction towards said cam;

said other projection being particularly adapted to be mutuallycooperatively engageable with a surface on said cam.

References Cited by the Examiner UNITED STATES PATENTS 7/52 Rinia et a1.-24 5/56 Dros et a1. 60--24

1. APPARATUS FOR CONTROLLING OUTPUT OF A FLUID-FYPE ENGINE IN WHICHWORKING FLUID TRANSVERSES A THERMODYNAMIC CYCLE OF COMPRESSION, HEATING,EXPANSION AND COOLING STAGES, SAID APPARATUS COMPRISING; A HOUSINGDEFINING A CHAMBER, SAID CHAMBER BEING DISPOSED TO RECEIVE A PORTION OFSAID WORKING FLUID THEREIN WITH SAID WORKING FLUID BEING COMMUNICABLEWITH SAID CHAMBER DURING THE COMPRESSION STAGE OF SAID CYCLE, AND MEANSFOR EFFECTIVE PRESSURE VARIATION IN SAID WORKING FLUID WITHIN SAIDCHAMBER.